US8752805B2 - Pressure control valve - Google Patents

Pressure control valve Download PDF

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Publication number
US8752805B2
US8752805B2 US13/387,659 US201013387659A US8752805B2 US 8752805 B2 US8752805 B2 US 8752805B2 US 201013387659 A US201013387659 A US 201013387659A US 8752805 B2 US8752805 B2 US 8752805B2
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US
United States
Prior art keywords
inflow
constriction
opening
valve
pressure control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
Application number
US13/387,659
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English (en)
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US20120186678A1 (en
Inventor
Martin Pilz
Benjin Luo
Mehmet-Fatih Sen
Frank Wauro
David Jayanth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JAYANTH, DAVID, WAURO, FRANK, LUO, BENJIN, PILZ, MARTIN, SEN, MEHMET-FATIH
Publication of US20120186678A1 publication Critical patent/US20120186678A1/en
Application granted granted Critical
Publication of US8752805B2 publication Critical patent/US8752805B2/en
Expired - Fee Related legal-status Critical Current
Adjusted expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/04—Devices for relieving the pressure on the sealing faces for sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0708—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides comprising means to avoid jamming of the slide or means to modify the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]

Definitions

  • the present invention relates to a pressure control valve.
  • the circumferential groove annular groove
  • a flow profile is produced which minimizes the hydraulic forces in the radial direction and thereby shortens the coupling filling time.
  • the groove according to the exemplary embodiments and/or exemplary methods of the present invention becomes noticeable particularly upon the “ripping open” of the inflow control edge. For, as soon as the inflow control edge “rips open”, that is, the inflow opening at least approximately releases, the fluid flows in the direction of the regulating opening.
  • the circumferential annular groove in the valve slide ensures a rapid pressure equalization in the circumferential direction of the valve slide, whereby a transverse hydraulic force acting on the valve slide is at least minimized.
  • the exemplary embodiments and/or exemplary methods of the present invention improve the flow of the hydraulic fluid, and instabilities at the inflow control edge are avoided.
  • the transverse forces mentioned in this instance are reduced, in addition, if the inflow opening does not include two radial channel bores, because of a circumferential annular groove in the housing, for example. This, however, is meaningful only if a flow on both sides is also provided in a valve block into which the pressure control valve is able to be inserted. Using this measure, the transverse hydraulic forces are also reduced. With respect to the reduction in the transverse force, it is naturally best if a multiplicity of inflow openings, that are situated uniformly distributed about the circumference, is provided in the form of radial channels.
  • the annular groove is at a distance from the inflow control edge.
  • the width of the annular groove is less than the width of the inflow opening. This particularly applies when the inflow opening is formed by a circumferential annular groove in the housing. Such a circumferential annular groove additionally contributes to a pressure equalization over the circumference of the valve slide.
  • the angle of a beveled edge of the constriction on the valve slide, at the inflow control edge, to a longitudinal axis of the valve slide is between 52° and 72°, and may more specifically be between 60° and 64°, and may very specifically be 62°.
  • This angle leads to a sufficiently great diversion of the hydraulic flow, that is first radial, without unwantedly strong turbulences and pressure losses occurring because of this diversion.
  • the constriction on the valve slide has a section that is curved concavely.
  • This concavely curved section leads to an additional gradual diversion of the hydraulic flow towards the regulating opening, which gradually takes place because of the concave curvature, and is therefore connected with only slight pressure losses.
  • the jet is guided along the curvature in such a way that the pressure control valve according to the present invention is able to be very dynamic, but also operates in a stable manner and reacts in an insensitive manner to interferences.
  • a radius of curvature of the concavely curved section of approximately 3.5 mm for this valve slide has turned out to be particularly advantageous, in this instance, this value, among other things, also depending on the properties of the hydraulic fluid and the general dimensions of the pressure control valve. It may also be a little larger or a little smaller, if necessary.
  • the abovementioned advantages are boosted even more if, because of the concavely curved section, the diameter of the constriction on the valve slide is at a minimum, and in the further course, after the curved section, the constriction has a section having a constant diameter.
  • the beginning of the section having a constant diameter is selected so that the jet, while flowing through the concave section, loses contact with the valve slide at exactly this location and flows on tangentially and impinges directly upon the inner annular groove of the regulating channel.
  • the section having the constant diameter be bordered by a radial wall section, at whose radial outer end a discharge control edge is formed which cooperates with a discharge opening in the housing.
  • the constriction extends from the inflow control edge to the discharge control edge, which also has advantages from the standpoint of production engineering. All-in all, an especially optimal flow profile is produced, with respect to the hydraulic forces, by the geometry thus provided of the constriction on the valve slide. In particular, the hydraulic forces are minimized in the axial direction, which shortens the coupling filling time during the application to a motor vehicle transmission.
  • Such a valve is thus able to function extremely dynamically, but, on the other hand, to be stable and insensitive to interferences.
  • FIG. 1 shows a longitudinal section through a pressure control valve.
  • FIG. 2 shows a detail II of FIG. 1 .
  • a pressure control valve bears overall reference numeral 10 . It is used for the control and operation of a hydraulic coupling in an automatic transmission that is not shown, for instance, in a stepped automatic transmission of a motor vehicle, or even for controlling or operating positioning cylinders in dual-clutch transmissions and CVT (continuously variable transmissions).
  • Pressure control valve 10 includes a flange housing 12 , in which a piston-like valve slide 14 is guided in a sliding manner. An end face 18 of valve slide 14 is able to be acted upon by an electromagnetic operating device 20 via a coupling pin 16 .
  • a pressure spring 24 engages, which is supported on a screw plug 26 of flange housing 12 .
  • pressure control valve 10 is connected fluidically to an inflow connection 28 , a regulating connection 30 , a discharge connection 32 and a return connection (“feedback channel”) 34 .
  • Return connection 34 and regulating connection 30 are fluidically connected to each other.
  • Inflow connection 28 is connected to a pressure source that is not shown in the drawings, such as a hydraulic pump.
  • Regulating connection 30 leads to the hydraulic coupling that is to be operated, and thus the hydraulic pressure, that is to be regulated, is present at regulating connection 30 .
  • Discharge connection 32 is connected to a low-pressure region.
  • flange housing 12 has four channels 36 to 42 that are axially at a distance from one another and run radially, which open out in annular grooves 44 to 50 assigned to them. Annular grooves 44 to 50 are configured in an inner wall surface of a guide bore 52 , in which valve slide 14 is guided in flange housing 12 .
  • Valve slide 14 has a section 54 , which has a reduced diameter, the course of the diameter being specific, and this will be explained more accurately below.
  • Section 54 of valve slide 14 will be designated below as a “constriction”, to simplify matters. It extends over the entire circumferential direction of valve slide 14 , and is thus rotationally symmetrical.
  • the constriction in section 54 is shown wider in the detail in FIG. 2 , it lies approximately opposite regulating annular groove 46 .
  • constriction 54 is bordered on its left side, as seen in FIG. 2 , by an inflow control edge 56 , which cooperates with inflow annular groove 44 in a manner that will be shown.
  • Constriction 54 is thus directly adjacent to inflow control edge 56 .
  • constriction 54 has a straight running beveled edge 58 , which is at an angle, with respect to a longitudinal axis 60 of valve slide 14 , of approximately 62°.
  • a concavely curved section 62 follows beveled edge 58 . Its radius of curvature in this case amounts to 3.5 mm. Because of concavely curved section 62 , the radius of valve slide 14 in the vicinity of constriction 54 is a minimum, in this case 2.5 mm. Concavely curved section 62 extends slightly beyond this minimum to a section 64 at a constant radius of 4 mm.
  • constriction 54 extends in the axial direction from inflow control edge 56 to discharge control edge 68 .
  • valve slide 14 has a circumferential annular groove 70 , which lies on the side of inflow control edge 56 facing away from constriction 54 and approximately opposite inflow annular groove 44 .
  • annular groove 70 has a square cross section having length of side of 2 mm. As seen in the axial direction of valve slide 14 , it is at a distance of approximately this quantity from inflow control edge 56 .
  • the width of annular groove 70 is less than the width of inflow annular grooves 44 .
  • Pressure control valve 10 works as follows: The desired pressure at regulating connection 30 is set by a corresponding application of current to electromagnetic operating device 20 .
  • valve slide 14 moves, which represents, to this extent, a “pressure balance”, to the right in FIGS. 1 and 2 , until discharge control edge 68 has reached discharge annular groove 48 , so that hydraulic fluid is able to flow away.
  • discharge annular groove 48 forms a discharge opening.
  • valve slide 14 moves to the left in FIGS. 1 and 2 , until inflow control edge 56 lies in the vicinity of inflow annular groove 44 . To this extent, inflow annular groove 44 forms an inflow opening.
  • annular groove 70 being axially positioned in valve slide 14 , pressure equalization is achieved over the circumference of valve slide 14 , which ensures a symmetrical inflow of hydraulic fluid in the direction of constriction 54 . Because of the special geometry of the contour of constriction 54 , a stable course of flow is additionally assured, which reduces flow forces acting in the axial direction of valve slide 14 . Hydraulic transverse forces in the dynamic operation of pressure control valve 10 are also reduced, particularly in the coupling filling process, that is, when a pressure increase at regulating connection 30 is desired.
  • section 64 having a constant diameter is selected so that the jet of hydraulic fluid, while flowing through concave section 62 , loses contact with valve slide 14 at exactly this location and flows on tangentially and impinges directly upon the inner annular groove or regulating annular groove 46 of regulating channel 38 . Finally, this assures a highly dynamic operation of the pressure control valve, which nevertheless operates in a stable manner and in an insensitive manner with respect to interferences.
  • a leakage connection is designated by 99 in FIG. 1 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)
US13/387,659 2009-07-29 2010-06-10 Pressure control valve Expired - Fee Related US8752805B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009028092 2009-07-29
DE102009028092A DE102009028092A1 (de) 2009-07-29 2009-07-29 Druckregelventil
DE102009028092.8 2009-07-29
PCT/EP2010/058141 WO2011012366A1 (fr) 2009-07-29 2010-06-10 Vanne de régulation de la pression

Publications (2)

Publication Number Publication Date
US20120186678A1 US20120186678A1 (en) 2012-07-26
US8752805B2 true US8752805B2 (en) 2014-06-17

Family

ID=42937095

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/387,659 Expired - Fee Related US8752805B2 (en) 2009-07-29 2010-06-10 Pressure control valve

Country Status (7)

Country Link
US (1) US8752805B2 (fr)
EP (1) EP2459908B1 (fr)
JP (1) JP5523567B2 (fr)
KR (1) KR101699571B1 (fr)
CN (1) CN102483168B (fr)
DE (1) DE102009028092A1 (fr)
WO (1) WO2011012366A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017129677A1 (de) * 2017-12-12 2019-06-13 Svm Schultz Verwaltungs-Gmbh & Co. Kg Schieberventil
US11713821B2 (en) * 2016-10-11 2023-08-01 Danfoss Power Solutions a.s,. Povazska, Slovakia Fluid control spool

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012223430A1 (de) 2012-12-17 2014-06-18 Robert Bosch Gmbh Elektromagnetisches Stellglied
DE102012224019A1 (de) 2012-12-20 2014-06-26 Robert Bosch Gmbh Schieberventil, insbesondere zur Steuerung eines Kraftfahrzeug-Automatikgetriebes
DE102013100717B3 (de) * 2013-01-24 2014-06-26 Kendrion (Villingen) Gmbh Elektromagnetisches Fluidventil
DE102014211648A1 (de) 2014-06-18 2015-12-24 Robert Bosch Gmbh Druckregelventil mit Einstellteil
DE102014214920A1 (de) 2014-07-30 2016-02-04 Robert Bosch Gmbh Schieberventil, mit einem Gehäuse und mit einem in einer Führungsausnehmung des Gehäuses angeordneten axial bewegbaren Ventilschieber
DE102015225927A1 (de) * 2015-12-18 2017-06-22 Robert Bosch Gmbh Ventilkolben und Schieberventil mit einem Ventilkolben
DE102021214388A1 (de) 2021-12-15 2023-06-15 Zf Friedrichshafen Ag Hydrauliksystem mit wenigstens zwei vorgesteuerten Druckregelventilen

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US3368791A (en) * 1964-07-14 1968-02-13 Marotta Valve Corp Valve with magnetic actuator
US3807454A (en) * 1972-12-15 1974-04-30 Gen Signal Corp Low effort plunger
US3990477A (en) * 1973-04-30 1976-11-09 Caterpillar Tractor Co. Force balanced valve spool
US4220178A (en) 1979-01-31 1980-09-02 The Cessna Aircraft Company Momentum balance spool
US4648803A (en) 1985-09-17 1987-03-10 Deere & Company Control circuit and control valve for radial piston pump
US4913172A (en) * 1988-12-19 1990-04-03 Fargo Chou Comb structure with ointment
EP0851160A1 (fr) 1996-12-26 1998-07-01 Ebara Corporation Procédé de compensation des forces hydrodynamiques et tiroir hydraulique utilisant ce procédé.
US6345804B1 (en) * 1999-04-14 2002-02-12 Hydraulik-Ring Gmbh Control valve for fuel injection devices for internal combustion engines
EP1197695A2 (fr) 2000-10-13 2002-04-17 Honda Giken Kogyo Kabushiki Kaisha Tiroir
JP2002122249A (ja) 2000-10-13 2002-04-26 Honda Motor Co Ltd スプールバルブ
JP2002130494A (ja) 2000-10-23 2002-05-09 Honda Motor Co Ltd スプールバルブ
CN1673591A (zh) 2004-03-25 2005-09-28 伊顿公司 具有缓冲蓄液器折流口的电磁控制滑阀及其制造方法
US20050217740A1 (en) * 2004-03-30 2005-10-06 Toyoda Koki Kabushiki Kaisha Solenoid valve
US7146998B2 (en) * 2001-11-09 2006-12-12 Honda Giken Kogyo Kabushiki Kaisha Hydraulic valve
WO2007020895A1 (fr) 2005-08-17 2007-02-22 Aisin Aw Co., Ltd. Dispositif de distributeur à triroir cylindrique
JP2007056910A (ja) 2005-08-22 2007-03-08 Aisin Aw Co Ltd ソレノイド駆動装置及びリニアソレノイドバルブ
US20090071545A1 (en) * 2005-03-17 2009-03-19 Xiaoning Xiang Automatic transmission having hydraulic valves with flow force compensation

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Publication number Priority date Publication date Assignee Title
JP2007092768A (ja) * 2005-09-27 2007-04-12 Aisin Seiki Co Ltd スプールバルブ

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3368791A (en) * 1964-07-14 1968-02-13 Marotta Valve Corp Valve with magnetic actuator
US3807454A (en) * 1972-12-15 1974-04-30 Gen Signal Corp Low effort plunger
US3990477A (en) * 1973-04-30 1976-11-09 Caterpillar Tractor Co. Force balanced valve spool
US4220178A (en) 1979-01-31 1980-09-02 The Cessna Aircraft Company Momentum balance spool
US4648803A (en) 1985-09-17 1987-03-10 Deere & Company Control circuit and control valve for radial piston pump
US4913172A (en) * 1988-12-19 1990-04-03 Fargo Chou Comb structure with ointment
EP0851160A1 (fr) 1996-12-26 1998-07-01 Ebara Corporation Procédé de compensation des forces hydrodynamiques et tiroir hydraulique utilisant ce procédé.
JPH10184963A (ja) 1996-12-26 1998-07-14 Ebara Corp 流体力補償方法およびスプール型流量制御弁
US6345804B1 (en) * 1999-04-14 2002-02-12 Hydraulik-Ring Gmbh Control valve for fuel injection devices for internal combustion engines
JP2002122249A (ja) 2000-10-13 2002-04-26 Honda Motor Co Ltd スプールバルブ
EP1197695A2 (fr) 2000-10-13 2002-04-17 Honda Giken Kogyo Kabushiki Kaisha Tiroir
US20020079002A1 (en) * 2000-10-13 2002-06-27 Akihiro Ueki Spool valve
JP2002130494A (ja) 2000-10-23 2002-05-09 Honda Motor Co Ltd スプールバルブ
US7146998B2 (en) * 2001-11-09 2006-12-12 Honda Giken Kogyo Kabushiki Kaisha Hydraulic valve
CN1673591A (zh) 2004-03-25 2005-09-28 伊顿公司 具有缓冲蓄液器折流口的电磁控制滑阀及其制造方法
US20050217740A1 (en) * 2004-03-30 2005-10-06 Toyoda Koki Kabushiki Kaisha Solenoid valve
US20090071545A1 (en) * 2005-03-17 2009-03-19 Xiaoning Xiang Automatic transmission having hydraulic valves with flow force compensation
WO2007020895A1 (fr) 2005-08-17 2007-02-22 Aisin Aw Co., Ltd. Dispositif de distributeur à triroir cylindrique
US20070051414A1 (en) 2005-08-17 2007-03-08 Aisin Aw Co., Ltd. Spool valve device
JP2007056910A (ja) 2005-08-22 2007-03-08 Aisin Aw Co Ltd ソレノイド駆動装置及びリニアソレノイドバルブ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713821B2 (en) * 2016-10-11 2023-08-01 Danfoss Power Solutions a.s,. Povazska, Slovakia Fluid control spool
DE102017129677A1 (de) * 2017-12-12 2019-06-13 Svm Schultz Verwaltungs-Gmbh & Co. Kg Schieberventil

Also Published As

Publication number Publication date
EP2459908A1 (fr) 2012-06-06
WO2011012366A1 (fr) 2011-02-03
JP2013500444A (ja) 2013-01-07
JP5523567B2 (ja) 2014-06-18
DE102009028092A1 (de) 2011-02-10
EP2459908B1 (fr) 2013-04-17
CN102483168B (zh) 2013-11-06
KR101699571B1 (ko) 2017-01-24
KR20120052248A (ko) 2012-05-23
CN102483168A (zh) 2012-05-30
US20120186678A1 (en) 2012-07-26

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